U.S. patent number 7,958,874 [Application Number 12/020,817] was granted by the patent office on 2011-06-14 for exhaust gas recirculation apparatus.
This patent grant is currently assigned to Denso Corporation. Invention is credited to Takashi Kobayashi, Osamu Shimane.
United States Patent |
7,958,874 |
Kobayashi , et al. |
June 14, 2011 |
Exhaust gas recirculation apparatus
Abstract
An exhaust gas recirculation apparatus includes a housing
connected with an EGR cooler via a mount face. The housing has a
valve chamber accommodating a selector valve. The housing has a
partition extending from the mount face close to the valve chamber
to divide first and second exhaust ports opened in the mount face.
A first passage leads exhaust gas into the EGR cooler through the
valve chamber. A second passage recirculates exhaust gas to the
intake passage through the EGR cooler and the valve chamber. A
bypass passage leads exhaust gas from the engine through the valve
chamber to bypass the EGR cooler. A rotation axis of the selector
valve is perpendicular to an axis of the mount face, and offset
away from the partition.
Inventors: |
Kobayashi; Takashi (Okazaki,
JP), Shimane; Osamu (Kariya, JP) |
Assignee: |
Denso Corporation (Kariya,
JP)
|
Family
ID: |
39587481 |
Appl.
No.: |
12/020,817 |
Filed: |
January 28, 2008 |
Prior Publication Data
|
|
|
|
Document
Identifier |
Publication Date |
|
US 20080184974 A1 |
Aug 7, 2008 |
|
Foreign Application Priority Data
|
|
|
|
|
Feb 5, 2007 [JP] |
|
|
2007-025085 |
Apr 23, 2007 [JP] |
|
|
2007-112518 |
|
Current U.S.
Class: |
123/568.17;
123/568.23; 123/568.12; 123/568.27; 123/568.29; 123/568.15;
123/568.25 |
Current CPC
Class: |
F02M
26/26 (20160201); F02M 26/51 (20160201); F02M
26/28 (20160201) |
Current International
Class: |
F02M
25/07 (20060101) |
Field of
Search: |
;123/568.12,568.11,568.13,568.17,568.18,568.23,568.25,568.27,568.29
;165/103 ;60/605.2 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Other References
Chinese Office Action dated Mar. 11, 2010, issued in corresponding
Chinese Application No. 200810009443.1, with English translation.
cited by other .
Chinese Office Action dated Sep. 2, 2010, issued in corresponding
Chinese Application No. 200810009443.1, with English translation.
cited by other.
|
Primary Examiner: Moulis; Thomas N
Assistant Examiner: Najmuddin; Raza
Attorney, Agent or Firm: Nixon & Vanderhye PC
Claims
What is claimed is:
1. An exhaust gas recirculation apparatus for recirculating exhaust
gas of an engine from an exhaust passage to an intake passage, the
apparatus comprising: an exhaust gas cooler for cooling exhaust gas
recirculated to the intake passage; a housing connected with the
exhaust gas cooler via a cooler mount face, the housing having a
valve chamber communicated with four exhaust ports including inlet
and outlet exhaust ports, the inlet and outlet exhaust ports being
adjacent to each other and opened in the cooler mount face, the
inlet exhaust port communicating with an inlet of the exhaust gas
cooler, the outlet exhaust port communicating with an outlet of the
exhaust gas cooler; a selector valve rotatably accommodated in the
valve chamber for controlling communication among the four exhaust
ports; and a rotation axis rotatably supporting the selector valve,
wherein the housing has a partition extending from the cooler mount
face close to the valve chamber, the partition dividing the inlet
and outlet exhaust ports, the housing has a first exhaust passage
that includes the inlet exhaust port, for leading exhaust gas from
the engine into the exhaust gas cooler through the valve chamber,
the housing further has a second exhaust passage that includes the
outlet exhaust port, for recirculating exhaust gas, which is cooled
in the exhaust gas cooler, to the intake passage through the valve
chamber, the housing further has a bypass passage for leading
exhaust gas from the engine through the valve chamber to bypass the
exhaust gas cooler, the rotation axis is substantially
perpendicular to a cooler-mount-face axis passing through a center
of the cooler mount face, the rotation axis is offset from a center
axis of the exhaust gas cooler and the cooler-mount-face axis of
the cooler mount face toward a center axis of the second exhaust
passage by a first predetermined offset amount, and the rotation
axis is offset to be farther away from the exhaust gas cooler than
the partition of the housing by a second predetermined offset
amount.
2. The apparatus according to claim 1, wherein the first exhaust
passage is inclined with respect to a center axis of the inlet
exhaust port, and the first exhaust passage substantially linearly
extends close to the inlet exhaust port.
3. The apparatus according to claim 1, wherein the rotation axis is
offset from the cooler-mount-face axis toward an
outlet-exhaust-port axis passing through a center of the outlet
exhaust port.
4. The apparatus according to claim 1, wherein the valve chamber
has a valve-chamber axis passing through a center of the valve
chamber, and the valve-chamber axis is offset from the
cooler-mount-face axis toward a an outlet-exhaust-port axis passing
through a center of the outlet exhaust port.
5. The apparatus according to claim 1, further comprising: a flow
control valve provided to the housing for controlling a flow of
exhaust gas recirculated to the intake passage; and an actuator
provided to the housing for driving the flow control valve.
6. The apparatus according to claim 5, wherein the housing and an
imaginary line, which is extended along a lateral side of the
housing perpendicularly to the cooler mount face, therebetween
define an actuator mount space for accommodating the actuator, and
the imaginary line is in parallel with an exhaust-gas-cooler axis
passing through a center of the exhaust gas cooler.
7. The apparatus according to claim 5, wherein the housing has an
actuator mount face via which the housing is connected with the
actuator, and the housing is formed of a metallic material having
heat resistance higher than heat resistance of the actuator.
8. The apparatus according to claim 1, wherein the housing has a
bypass passage wall separating the bypass passage from an exterior
of the housing, the housing further has a cooler introduction
passage wall separating the first exhaust passage from the exterior
of the housing, and the bypass passage wall is thicker than the
cooler introduction passage wall.
9. The apparatus according to claim 1, wherein the housing has a
bypass passage wall separating the bypass passage from an exterior
of the housing, the housing further has a cooler introduction
passage wall separating the first exhaust passage from the exterior
of the housing, and the cooler introduction passage wall is thinner
than the bypass passage wall.
10. The apparatus according to claim 8, wherein the housing has a
radiating portion exposed to an outer surface of the cooler
introduction passage wall, and the radiating portion is adapted to
dissipate heat of exhaust gas, which flows through the first
exhaust passage, to air passing over an outer surface of the cooler
introduction passage wall.
11. The apparatus according to claim 1, wherein the partition of
the housing has an end located in the valve chamber, and the
rotation axis is located farther from the exhaust gas cooler than
the end of the partition.
12. The apparatus according to claim 11, wherein the end of the
partition extends from the partition in an extended direction, and
the rotation axis is spaced from the end of the partition in the
extended direction.
13. The apparatus according to claim 12, wherein the rotation axis
is located on an extension line extended from the end of the
partition in the extended direction.
Description
CROSS REFERENCE TO RELATED APPLICATIONS
This application is based on and incorporates herein by reference
Japanese Patent Applications No. 2007-25085 filed on Feb. 5, 2007
and No. 2007-112518 filed on Apr. 23, 2007.
FIELD OF THE INVENTION
The present invention relates to an exhaust gas recirculation
apparatus for recirculating exhaust gas of an internal combustion
engines from an exhaust passage to an intake passage.
BACKGROUND OF THE INVENTION
Conventionally, an EGR system (exhaust gas recirculation apparatus)
is provided to an internal combustion engine such as a diesel
engine. The EGR system is adapted to recirculating a part of
exhaust gas (EGR gas) of the engine from an exhaust passage to an
intake passage so as to reduce emission of the engine. EGR gas
contains a large amount of inert gas such as steam, carbon dioxide,
and the like after combustion. The EGR system is capable of
effectively reducing combustion temperature of the engine, thereby
effectively reducing a toxic substance such as nitrogen oxide (NOx)
contained in exhaust gas.
The EGR system includes an EGR flow control valve (EGRV) midway
through an EGR pipe, which leads EGR gas from the exhaust passage
to recirculate the EGR gas to the intake passage. The EGRV controls
an amount of the EGR gas returning to the intake passage through an
GFR passage in the EGR pipe. The EGR system includes an exhaust gas
cooler (EGR cooler) midway through the EGR pipe. The EGR cooler may
be a water cooling type heat exchanger. The EGR cooler cools EGR
gas, which returns to the intake passage, thereby enhancing a
charging efficiency of the engine. Thus, emission of the engine can
be effectively reduced.
In the above cooled EGR system, EGR gas is cooled through the EGR
cooler, and the cooled gas is recirculated into the intake passage.
In view of further emission regulations of an engine such as a
diesel engine, a hot EGR system is further needed in addition to
the cooled EGR system. The hot EGR system is adapted to leading EGR
gas as hot EGR gas to bypass the EGR cooler, and returning the hot
EGR gas into the intake passage. The hot EGR system is capable of
enhancing combustion in the engine when the engine is started in
the cold condition or in regeneration of a diesel particulate
filter (DPF).
Specifically, the hot EGR system has a bypass passage in parallel
with an EGR passage. EGR passage leads EGR gas from the exhaust
passage to recirculate the EGR gas to the intake passage through
the EGR cooler. The bypass passage leads EGR gas to bypass the EGR
cooler. The hot EGR system is adapted to recirculating EGR gas to
the intake passage without passing through the EGR cooler in an
engine starting or the like.
Regeneration of the DPF is performed by supplying hot exhaust gas
to the DPF so as to heat the DPF such that temperature of the DPF
becomes greater than combustion temperature of a particulate matter
(PM). The hot EGR system is capable of leading hot EGR gas into the
intake passage, thereby enhancing heating of the DPF in
regeneration. The hot EGR system is also capable of increasing
temperature of intake air drawn into the combustion chamber of the
engine. Therefore, the hot EGR system is capable of further
effectively heating exhaust gas supplied to the DPF, thereby
further effectively reducing emission of the engine.
According to EP0987427, an EGR system is capable of manipulating a
flow of cooled EGR gas and a flow of hot EGR gas so as to control
temperature of EGR gas returning to an intake passage.
As shown in FIG. 9, the EGR system includes an EGR module
constructed of an EGR cooler 101, a housing 102, two passage
selector valves (valve plates) 103, 104, a rotation axis 105, and a
negative pressure controlled actuator 106. The EGR cooler 101 cools
EGR gas using engine cooling water. The housing 102 has therein two
first and second valve chambers. The two passage selector valves
(valve plates) 103, 104 are respectively accommodated in the first
and second valve chambers of the housing 102. The rotation axis 105
supports the passage selector valves 103, 104. The negative
pressure controlled actuator 106 drives the rotation axis 105 to
manipulate the passage selector valves 103, 104. The EGR cooler 101
has a U-shaped EGR passage having two parallel passages connected
via a U-shaped portion. The passage selector valve 103 is coupled
to the rotation axis 105 such that the passage selector valve 103
accommodated in the first valve chamber and the passage selector
valve 104 accommodated in the second valve chamber form a relative
angle (phase difference) of 70 to 90.degree..
In the present structure, a branch pipe is provided upstream of the
housing 102, and a junction pipe is provided downstream of the
housing 102 with respect to the flow direction of EGR gas. The
housing 102 of the two passage selector valves 103, 104 does not
have a branch portion and a junction portion, i.e., merge
portion.
The housing 102 has a cooler mount face, a branch-pipe mount face,
and a junction pipe mount face respectively provided with two of
six EGR ports 111 to 116. The EGR ports 111, 112 are communicated
with the first valve chamber. The EGR ports 115, 116 are
communicated with the second valve chamber.
The housing 102 has an EGR passage and a bypass passage 123
adjacently extending in parallel with each other. The EGR passage
(main passage) leads exhaust gas of the internal combustion engine
so as to recirculate the exhaust gas to the intake passage through
the EGR cooler 101. The bypass passage 123 leads exhaust gas from
the internal combustion engine to recirculate the exhaust gas to
the intake passage through the second valve chamber so as to
bypasses the EGR cooler 101.
The EGR passage has a cooler inlet gas passage 121 and a cooler
outlet gas passage 122. The cooler inlet gas passage 121 leads hot
EGR gas discharged from the internal combustion engine into the EGR
cooler 101 through the first valve chamber. The cooler outlet gas
passage 122 recirculates cooled EGR gas, which is cooled through
the EGR cooler 101, to the intake passage.
A partition 124 connects the cooler mount face, to which the EGR
cooler 101 is attached, with the passage wall surface defining the
bypass passage 123. The partition 124 divides the interior of the
housing 102 into the EGR passage and the bypass passage 123. The
EGR passage includes the cooler inlet gas passage 121 and the
cooler outlet gas passage 122.
In view of mountability to an engine, an EGR module is needed to be
downsized by integrating an EGR cooler, a passage selector valve,
and EGRV. The EGR module disclosed in EP0987427 has the two passage
selector valves 103, 104 provided in the two parallel passages, and
the two passage selector valves 103, 104 are connected with the
single rotation axis 105. In the present structure, the EGR module
is enlarged, and hence mountability to a vehicle such as a car, in
particular, an engine is impaired.
In addition, in the EGR module of EP0987427, the cooler mount face
is directly connected with the passage wall surface of the bypass
passage 123 via the partition 124 of the housing 102. In addition,
the rotation axis 105 of the two passage selector valves 103, 104
is in parallel with the axes of the EGR cooler 101 and the housing
102 passing through the center of the cooler mount face. One end of
the rotation axis 105 is rotatably supported by a bearing 125
provided in the vicinity of the cooler mount face.
In the present structure, the bypass passage wall surface is
directly exposed to hot EGR gas passing through the bypass passage
123, and accordingly, temperature of the bypass passage wall
surface increases. The rotation axis 105 and the partition 124 of
the housing 102 may be formed of a thermally conductive material.
In EP0987427, the housing 102 is formed of an aluminum material. In
this case, temperature of the partition 124 of the housing 102
significantly increases due to thermal conduction from hot EGR
gas.
When temperature of the partition 124 of the housing 102 increases,
temperature of the cooler mount face of the housing 102 also
increases. Consequently, temperature of the EGR cooler 101
increases due to heat conduction via the cooler mount face of the
housing 102. That is, in the structure of EP0987427, heat of hot
EGR gas passing through the bypass passage 123 is easily conducted
to the EGR cooler 101 of the EGR module.
When the hot EGR mode is switched to the cooled EGR mode by
manipulating the rotation angle of the two passage selector valves
103, 104, cooled EGR gas is recirculated to the intake passage
through the EGR cooler 101. In this condition, even engine cooling
water is recirculated inside the EGR cooler 101, cooling
performance of the EGR cooler 101 is impaired due to thermal
conduction from hot EGR gas in the hot EGR mode. As a result,
emission cannot be sufficiently reduced.
In addition, when cooled EGR gas and hot EGR gas are mixed and
returned to the intake passage so as to control temperature of EGR
gas corresponding to the operating condition of the engine, the
partition 124 of the housing 102 is transmitted with heat from hot
EGR gas passing through the bypass passage 123. Accordingly, the
hot EGR gas exerts influence to cooled EGR gas passing through the
cooler outlet gas passage 122. Consequently, temperature of the
cooled EGR gas passing through the cooler outlet gas passage 122
increases. Accordingly, it is hard to control temperature of
mixture of hot EGR gas and cooled EGR gas, which returns to the
intake passage. As a result, emission cannot be sufficiently
reduced,
SUMMARY OF THE INVENTION
In view of the foregoing and other problems, it is an object of the
present invention to produce an exhaust gas recirculation apparatus
that includes an exhaust gas cooler having enhanced cooling
performance to reduce emission. It is another object of the present
invention to produce an exhaust gas recirculation apparatus being
readily mounted to an internal combustion engine.
According to one aspect of the present invention, an exhaust gas
recirculation apparatus for recirculating exhaust gas of an engine
from an exhaust passage to an intake passage, the apparatus
comprises an exhaust gas cooler for cooling exhaust gas
recirculated to the intake passage. The apparatus further comprises
a housing connected with the exhaust gas cooler via a cooler mount
face, the housing having a valve chamber communicated with four
exhaust ports including first and second exhaust ports, the first
and second exhaust ports being adjacent to each other and opened in
the cooler mount face. The apparatus further comprises a selector
valve rotatably accommodated in the valve chamber for controlling
communication among the four exhaust ports. The apparatus further
comprises a rotation axis rotatably supporting the selector valve.
The housing has a partition extending from the cooler mount face
close to the valve chamber, and the partition dividing the first
and second exhaust ports. The housing has a first exhaust passage
for leading exhaust gas from the engine into the exhaust gas cooler
through the valve chamber. The housing further has a second exhaust
passage for recirculating exhaust gas, which is cooled in the
exhaust gas cooler, to the intake passage through the valve
chamber. The housing further has a bypass passage for leading
exhaust gas from the engine through the valve chamber to bypass the
exhaust gas cooler. The rotation axis is substantially
perpendicular to a cooler-mount-face axis passing through a center
of the cooler mount face. The rotation axis is offset away from the
partition of the housing.
BRIEF DESCRIPTION OF THE DRAWINGS
The above and other objects, features and advantages of the present
invention will become more apparent from the following detailed
description made with reference to the accompanying drawings. In
the drawings:
FIG. 1 is a sectional view showing an EGR module according to a
first embodiment;
FIG. 2 is a perspective view showing the EGR module according to
the first embodiment;
FIG. 3 is a sectional view showing a valve unit of the EGR module,
according to the first embodiment;
FIG. 4 is a sectional view showing the EGR module in a cooled EGR
mode, according to the first embodiment;
FIG. 5 is a sectional view showing the EGR module in a hot EGR
mode, according to the first embodiment;
FIG. 6 is a sectional view showing the EGR module in a hot-cooled
EGR mixing mode, according to the first embodiment;
FIG. 7 is a sectional view showing an EGR module in a cooled EGR
mode, according to a second embodiment;
FIG. 8 is a sectional view showing the EGR module in a hot EGR
mode, according to the second embodiment; and
FIG. 9 is a sectional view showing an EGR module according to a
prior art.
DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
First Embodiment
(Construction)
As shown in the FIGS. 1 to 6, in the present embodiment, an
internal combustion engine such as a diesel engine is provided with
an exhaust gas recirculation system (EGR system) including an
exhaust gas recirculation pipe (EGR pipe) and EGR module, for
example. The EGR pipe recirculates exhaust gas as EGR gas partially
from an exhaust passage of the engine to an air intake passage of
the engine. The EGR module is provided midway through the EGR
pipe.
The present EGR module includes an exhaust gas cooling device (EGR
cooling device) and an exhaust gas control device (EGR control
device). The EGR cooling device cools EGR gas recirculated from the
exhaust passage to the air intake passage. The EGR control device
controls a flow amount and temperature of EGR gas recirculated from
the exhaust passage to the air intake passage. The EGR module is
constructed by integrating an EGR cooler 1 as an exhaust gas cooler
with a valve unit 2. The valve unit 2 is provided with first and
second exhaust gas control valves for controlling the flow and
temperature of EGR gas.
The valve unit 2 includes a common housing 3 of the first and
second exhaust gas control valves. The housing 3 therein defines an
exhaust gas passage (EGRV passage) through which EGR gas flows. The
EGRV passage includes first and second EGR passages 4, 5 and a
bypass passage 6. The EGRV passage (main channel, main route)
defines an exhaust gas passage including the first and second EGR
passages 4, 5 for recirculating EGR gas. The EGR gas flows from the
exhaust passage into the housing 3, and recirculated into the air
intake passage through the EGR cooler 1. The bypass passage 6 as
the exhaust gas passage defines an EGRV passage (bypass passage,
bypass route) for recirculating EGR gas from the exhaust passage to
the air intake passage through the housing 3 by bypassing the EGR
cooler 1.
The structure of the housing 3 will be described later in detail.
An exhaust gas flow control valve (EGR flow control valve, EGRV) as
a first exhaust gas control valve controls the flow of the EGR gas
passing through the EGRV passage inside the housing 3. In the
present embodiment, the EGRV is mounted in the housing 3 commonly
with the second exhaust gas control valve. The EGRV includes a
first valve (EGR flow rate control valve, flow control valve) 11, a
first rotation axis (valve shaft) 12, and a first actuator main
body (actuator) 13. The flow control valve 11 is inserted in the
EGRV passage of the housing 3. The valve shaft 12 supports the flow
control valve 11. The first actuator main body 13 drives the flow
control valve 11 via the valve shaft 12. The EGRV is described
later in detail. An exhaust gas selector valve (EGR selector valve)
as the second exhaust gas control valve is provided for controlling
temperature of EGR gas flowing through the EGRV passage of the
housing 3.
In the present embodiment, the EGR selector valve is provided in
the housing 3 commonly with the EGRV. The EGR selector valve
includes a four-way selector valve 14, a second rotation axis as a
valve shaft 15, and a second actuator main body 16. The four-way
selector valve 14 is inserted in the EGRV passage of the housing 3
downstream of the flow control valve 11 (FIG. 3) with respect to
the EGR gas flow. The valve shaft 15 supports the four-way selector
valve 14. The second actuator main body 16 drives the four-way
selector valve 14 via the valve shaft 15.
The EGR selector valve is described later in detail. In the present
embodiment, the valve unit 2 is constructed of the housing 3, the
EGRV, and the EGR selector valve. The EGR cooler 1 is a
water-cooling exhaust gas cooler for conducting heat exchange
between engine cooling water, which flows from an engine water
jacket, and EGR gas, thereby cooling the EGR gas to temperature
less than predetermined temperature. The EGR cooler 1 is airtightly
joined with a cooler mount face of the housing 3.
The EGR cooler 1 includes a casing and a stacked core portion (not
shown). The casing is in the shape of a rectangular pipe having one
axial open end. The stacked core portion is constructed by stacking
multiple flat tubes in the thickness direction thereof, and the
flat tubes are adapted to leading EGR gas. Each flat tube is
inserted with an offset-type inner fin for enhancing heat exchange.
Each flat tube has a U-shaped EGR passage 20 (FIGS. 4, 6) having
two parallel passages connected via a U-shaped portion. The stacked
core portion has multiple cooling-water passages (not shown)
through which engine cooling water circulates around the
circumference of the multiple flat tubes.
The casing of the EGR cooler 1 has a cooling-water inlet hole and a
cooling-water outlet hole. The cooling-water inlet hole of the
casing is connected with an inlet pipe 21 for leading engine
cooling water into the multiple cooling-water passages. The
cooling-water outlet hole of the casing is connected with an outlet
pipe 22 for leading engine cooling water from the multiple
cooling-water passages. The upper wall of the casing and the
stacked core portion therebetween define an inlet tank chamber and
an outlet tank chamber, which were divided with a partition (not
shown). The inlet tank chamber communicates the cooling-water inlet
hole of the casing with the multiple cooling-water passages. The
outlet tank chamber communicates the cooling-water outlet hole of
the casing with the multiple cooling-water passages.
The casing has an end on the side of the housing, and the end is
integrally formed with a joint portion, which has a joint face
joined with the cooler mount face of the housing 3. The joint
portion has an exhaust gas inlet hole (EGR inlet hole) and an
exhaust gas outlet hole (EGR outlet hole) on the housing mount
face. The EGR inlet hole serves as an inlet of the EGR cooler 1,
and the EGR outlet hole serves as an outlet of the EGR cooler 1.
The inlet and the outlet of the EGR cooler 1 communicate with the
U-shaped EGR passage 20 of each stacked core portion.
The joint portion of the casing has a flange 23 radially projected
beyond the outer wall of the casing. The flange 23 has multiple
bolt holes (not shown) each inserted with a screw bolt 24. The EGR
cooler 1 is screwed to the cooler mount face of the housing 3 with
the screw bolts 24 in a state where the housing mount face of the
joint portion of the casing is tightly in contact with the cooler
mount face of the housing 3. A sealing member such as a gasket or a
packing may be interposed between the housing mount face of the EGR
cooler 1 and the cooler mount face of the housing 3 so as to
restrict leakage of EGR gas.
The housing 3 is integrally formed of a metallic material such as
cast iron to be in a predetermined shape. The housing 3 is provided
midway through the EGR pipe. The housing 3 includes a block 25 as a
housing body having a hollow portion as a valve chamber 7. The
block 25 has a cooler mount face 26, to which the flange 23 of the
joint portion of the EGR cooler 1 is attached. In the present
embodiment, the block 25 is integrally formed with a cylindrical
inlet pipe 27 and a cylindrical outlet pipe 29. The inlet pipe 27
is projected from the block 25 toward the exhaust passage upstream
with respect to the flow direction of EGR gas. The outlet pipe 29
is projected from the block 25 toward the air intake passage
downstream with respect to the flow direction of EGR gas.
The valve chamber 7 is communicated with Tour exhaust gas ports.
The four exhaust gas ports include an EGR introduction port 30,
which has a circular cross section, first and second EGR ports 31,
32, each of which has a rectangular cross section, and an EGR
delivery port 33, which has a circular cross section, and the like.
The first and second EGR ports 31, 32 are in parallel with each
other and open in the cooler mount face 26 of the housing 3. The
first EGR port 31 as a cooler inlet port is opposed to the inlet of
the EGR cooler 1. The second EGR port 32 as a cooler outlet port is
opposed to the outlet of the EGR cooler 1.
A rectangular flange 34 (FIG. 2) is integrally formed with the
periphery of the cooler mount face 26 of the block 25. The flange
34 has multiple bolt holes each screwed with the screw bolt 24. The
valve chamber 7 of the block 25 has a lateral side portion having a
communication hole extending along a rotation axis of the valve
shaft 15 of the four-way selector valve 14. The communication hole
is provided inside a plug 35. The plug 35 airtightly blockades a
circular opening in an outer wall of the housing 3.
The inlet pipe 27 has a first joint face upstream of the valve
chamber 7 with respect to the flow direction of EGR gas. The inlet
pipe 27 is attached to an EGR pipe on the side of an exhaust
passage or a branch portion of the engine exhaust pipe, in
particular a branch portion of the exhaust manifold, via the first
joint face. The outer circumferential periphery of the inlet pipe
27 has a flat actuator mount face 36 to which the first actuator
main body 13 is mounted. The inlet pipe 27 has a communication hole
37. The communication hole 37 extends along the rotation axis of
the valve shaft 12 of the flow control valve 11 to communicate the
actuator mount face 36 with a wall surface defining the passage in
the inlet pipe 27.
The outer circumferential periphery of an opening end of the inlet
pipe 27 is integrally formed with multiple protrusions 39. The
protrusions 39 respectively have screw holes 40 into which screw
bolts are screwed to fix the inlet pipe 27 with an EGR pipe on the
side of the exhaust passage. The outlet pipe 29 has a second joint
face downstream of the valve chamber 7 with respect to the flow
direction of EGR gas. The outlet pipe 29 is attached to an EGR pipe
on the side of the intake passage or a merge portion of the engine
intake pipe, in particular a merge portion of the intake
manifold.
The first EGR passage 4 as a first exhaust gas passage (cooler
introduction path) leads EGR gas into the EGR cooler 1 through the
valve chamber 7. The first EGR passage 4 has an inclined passage,
which substantially linearly extends from a portion in the vicinity
of the EGR introduction port 30 toward the first EGR port 31. The
inclined passage of the first EGR passage 4 is inclined with
respect to a center axis of the first EGR port 31. The center axis
of the first EGR port 31 passes through the center of the first EGR
port 31.
The second EGR passage 5 as a second exhaust gas passage (cooler
delivery path) leads EGR gas cooled in the EGR cooler 1 to
recirculate the EGR gas into the intake passage through the valve
chamber 7. The second EGR passage 5 has a bent passage, which is
bent in the valve chamber 7 at a substantially right angle. The
second EGR passage 5 may have a curve passage, which gently curves
in the bent passage. The bypass passage 6 as a cooler bypass
passage (cooler bypass path) leads EGR gas through the valve
chamber 7 to bypass the EGR cooler 1. The bypass passage 6 has a
bent passage, which is bent in the valve chamber 7 at a
substantially right angle. The bypass passage 6 may have a curve
passage, which gently curves in the bent passage.
The first EGR passage 4 and the bypass passage 6 have the EGR
introduction port 30 upstream of the valve chamber 7 with respect
to the flow direction of EGR gas. The EGR introduction port 30
opens in the first joint face of the housing 3. The first EGR
passage 4 and the bypass passage 6 commonly have both the EGR
introduction port (common exhaust gas inlet) 30 and a first
communication passage (first common passage) 41, which communicates
the EGR introduction port 30 with the valve chamber 7.
The first EGR passage 4 has the first EGR port 31 downstream of the
valve chamber 7 with respect to the flow direction of EGR gas. The
first EGR port 31 opens in the cooler mount face 26 of the housing
3. In the present embodiment, a first communication passage 42 is
provided in the vicinity of the cooler mount face 26 of the housing
3 to communicate the valve chamber 7 with the first EGR port 31.
The second EGR passage 5 has the second EGR port 32 upstream of the
valve chamber 7 with respect to the flow direction of EGR gas. The
second EGR port 32 opens in the cooler mount face 26 of the housing
3. In the present embodiment, a second communication passage 43 is
provided in the vicinity of the cooler mount face 26 of the housing
3 to communicate the second EGR port 32 with the valve chamber
7.
The second EGR passage 5 and the bypass passage 6 have the EGR
delivery port 33 downstream of the valve chamber 7 with respect to
the flow direction of EGR gas. The EGR delivery port 33 opens in
the second joint face of the housing 3. The second EGR passage 5
and the bypass passage 6 commonly have both the EGR delivery port
(common exhaust gas outlet) 33 and a second communication passage
(second common passage) 44, which communicates the valve chamber 7
with the EGR delivery port 33.
The housing 3 has a Y-shaped partition wall 45 (FIG. 1) to divide
the first EGR passage 4 from the second EGR passage 5. The housing
3 has a partition 9 as a part of the partition wall 45. The
partition 9 is in a bent shape to divide the first EGR port 31 from
the second EGR port 32. The partition 9 airtightly partitions the
first communication passage 42, which has the first EGR port 31 on
the side of the cooler mount face 26 with respect to the valve
chamber 7, from the second communication passage 43 including the
second EGR port 32. The partition wall 45 has an opening 46, which
communicates the first EGR passage 4 with the second EGR passage
5.
The partition 9 extends from the cooler mount face 26 toward the
valve chamber 7. The partition 9 includes a linear portion and an
inclined portion. The liner portion of the partition 9 extends
along the center axis of the EGR cooler l, the center axis of the
EGR cooler 1 passing through the center of the joint face of the
EGR cooler 1 perpendicularly to the joint face of the EGR cooler 1.
The liner portion of the partition 9 is on the same axis as the
center axis (cooler-mount-face axis) X of the cooler mount face 26
passing through the center of the cooler mount face 26. The
inclined portion of the partition 9 is on the same axis as the axis
passing through the center of the center of the opening 46, i.e.,
the center of the valve chamber 7. The partition 9 has an
intermediate portion between the linear portion and the inclined
portion, and the partition 9 is bent at the intermediate portion.
The inclined portion of the partition 9 is inclined a predetermined
angle of inclination toward the center axis (second-exhaust-port
axis) Y of the second EGR port 32 of the center axis Y passing
through the center of the second EGR port 32 with respect to the
center axis of the EGR cooler 1 and the center axis X of the cooler
mount face 26.
The valve chamber 7 of the housing 3 has the center, which
corresponds to the center of the opening 46. The center of the
valve chamber 7 is offset from the center axis of the EGR cooler 1
and the center axis X of the cooler mount face 26 to the center
axis Y of the second EGR port 32 by a predetermined offset amount.
The center of the valve chamber 7 is offset away from the partition
of the housing 3 by a predetermined offset amount. The valve
chamber 7 of the housing 3 has first to fourth communication holes.
The first communication hole communicates with the EGR introduction
port 30 through the first communication passage 41. The second
communication hole communicates with the first EGR port 31 through
the first communication passage 42. The third communication hole
communicates with the second EGR port 32 through the second
communication passage 43. The fourth communication hole
communicates with the EGR delivery port 33 through the second
communication passage 44.
The block 25 of the housing 3 is provided with an EGR temperature
sensor 49 (FIG. 2) such as a thermistor. The EGR temperature sensor
49 detects temperature of EGR gas, which flows from the outlet of
the EGR cooler 1 into the second EGR passage 5 (second
communication passage 43) through the second EGR port 32. The EGR
temperature sensor 49 converts the temperature of EGR gas into an
electric signal, and outputs the electric signal to an engine
control unit (ECU).
The partition 9 of the housing 3 has a first valve seat portion 51.
The four-way selector valve 14 has a seal portion, and the seal
portion is seated to the first valve seat portion 51 when the
four-way selector valve 14 communicates the first and second EGR
passages 4, 5 and blocks the bypass passage 6. The housing 3 has a
passage wall surface opposed to the first valve seat portion 51 via
the second communication hole, and the passage wall surface has a
second valve seat portion 52. The seal portion of the four-way
selector valve 14 is seated to the second valve seat portion 52
when the four-way selector valve 14 blocks the two first and second
EGR passages 4, 5 and communicates the bypass passage 6.
The EGRV includes the flow control valve 11, the valve shaft 12,
the spring (not shown), and the first actuator main body 13. The
flow control valve 11 is accommodated in the first communication
passage (EGRV passage) 41 of the housing 3 such that the flow
control valve 11 is capable of opening and closing the first
communication passage 41. The flow control valve 11 rotates
integrally with the valve shaft 12. The spring (not shown) biases
the flow control valve 11 to a closing direction. The first
actuator main body 13 manipulates the flow control valve 11. The
flow control valve 11 is rotated around the rotation axis of the
valve shaft 12 and the rotation angle of the flow control valve 11
is changed, such that the flow control valve 11 continuously
changes the opening of the first communication passage 41 of the
housing 3. Thus, the flow control valve 11 arbitrarily and variably
controls the flow amount of EGR gas returning from the exhaust
passage into the intake passage.
The flow control valve 11 is fixed to a tip end of the valve shaft
12 in a state where the flow control valve 11 is inclined with
respect to the valve shaft 12 at a predetermined angle of
inclination. The flow control valve 11 has an outer circumference
end surface equipped with a seal ring 53. The inner wall surface of
the inlet pipe 27 of the housing 3 is press-fitted with a
cylindrical nozzle 54 formed of a metallic material such as
stainless steel excellent in heat resistance and corrosion
resistance. The nozzle 54 is inserted in only a sliding part on
which a sliding surface of the seal ring 53 slides when the flow
control valve 11 is rotated around a full-close position.
The valve shaft 12 of the flow control valve 11 is inserted
straight along the axis of the communication hole 37 to pass
through the communication hole 37. The valve shaft 12 is extends
from the outside of the inlet pipe 27 of the housing 3 into the
inside of the first communication passage 41.
The first actuator main body 13 is a housing member having an
opening closed with a sensor cover 55. The first actuator main body
13 is formed by die-casting of aluminum alloy, which contains
aluminum as a main component. The first actuator main body 13 is
screwed with multiple screw bolts tightly to the actuator mount
face 36 of the inlet pipe 27 of the housing 3, thereby joined with
the housing 3. The first actuator main body 13 accommodates an
electric motor and a transmission device The electric motor such as
a DC motor generates driving force by being supplied with
electricity. The transmission device such as reduction gears
transmits the driving force of the electric motor to the valve
shaft 12. An oil seal, a ball bearing, or the like is press-fitted
between the valve shaft 12 of the flow control valve 11 and a
bearing of the first actuator main body 13.
As shown in FIG. 3, a bearing member such as a bushing 57 is
press-fitted between the inlet pipe 27 of the housing 3 and the
valve shaft 12 of the flow control valve 11. The bushing 57 has a
slide hole for rotatably supporting the valve shaft 12 of the flow
control valve 11. The outer circumferential periphery of the valve
shaft 12 and the inner circumferential periphery of the wall
surface of the slide hole of the bushing 57 therebetween define a
substantially cylindrical gap (clearance), via which the valve
shaft 12 is rotatably supported by the bushing 57, A sealing member
such as a gasket or a packing is interposed between the actuator
mount face 36 of the inlet pipe 27 of the housing 3 and a housing
joint face of the first actuator main body 13 so as to restrict
leakage of EGR gas.
In the present embodiment, an EGR flow rate sensor is mounted to
the first actuator main body 13. The EGR flow rate sensor converts
rotation angle (valve opening) of the flow control valve 11 into an
electric signal, and outputs the electric signal, which indicates
the valve opening of the flow control valve 11, to the ECU. In the
present structure, in addition to the first actuator main body 13,
the EGR flow rate sensor is mounted to the housing 3 of the EGR
module.
The EGR selector valve is constructed of the four-way selector
valve 14, the valve shaft 15, and the second actuator main body 16.
The four-way selector valve 14 is rotatably accommodated in the
valve chamber 7 of the housing 3 such that the four-way selector
valve 14 is capable of switching the passages. The valve shaft 15
rotates together with the four-way selector valve 14. The second
actuator main body 16 drives the four-way selector valve 14. The
four-way selector valve 14 is formed of a metallic material such as
stainless steel excellent in heat resistance and corrosion
resistance. The four-way selector valve 14 is rotatable in the
valve chamber 7 of the housing 3. The four-way selector valve 14
arbitrarily switches communication among four exhaust ports by
rotating around the rotation axis of the valve shaft 15 in the
valve chamber 7.
The four-way selector valve 14 is a butterfly valve constructed of
valve plates each being in a rectangular shape. The valve plates of
the four-way selector valve 14 are extended toward both sides
perpendicularly to the rotation axis of the valve shaft 15. That
is, the valve plates are extended toward both sides along the
radial direction of the rotation axis of the valve shaft 15. The
valve plates of the four-way selector valve 14 include first and
second metal plates 61, 62. The first metal plate 61 has an
outermost portion provided with a seal portion, which is seated
selectively to one of the first and second valve seat portions 51,
52.
The four-way selector valve 14 is capable of variably controlling
openings of the first and second EGR passages 4, 5 and the bypass
passage 6 according to the switching position thereof. In the
present structure, the four-way selector valve 14 is capable of
variably controlling a mixing ratio between cooled EGR gas and hot
EGR gas. The cooled EGR gas is cooled in the EGR cooler 1 when
passing through the first and second EGR passages 4, 5. The hot EGR
gas passes through the bypass passage 6 to bypass the EGR cooler.
Thus, the four-way selector valve 14 is capable of controlling
temperature of EGR gas, which returns to the intake passage.
As shown in FIG. 4, in a cooled EGR mode, the four-way selector
valve 14 as a partition plate divides the valve chamber 7 into the
first EGR passage 4 and the second EGR passage 5. In the cooled EGR
mode, the four-way selector valve 14 manipulates the communication
among the four exhaust gas ports to form the first and second EGR
passages 4, 5 inside the housing 3.
As shown in FIGS. 1, 5, in a hot EGR mode, the four-way selector
valve 14 as a partition plate divides the valve chamber 7 into a
portion on the side of the EGR cooler 1 and a portion on the side
of the bypass passage 6. That is, in the hot EGR mode, the four-way
selector valve 14 divides the valve chamber 7 into a portion on the
side of the partition 9 of the housing 3 and a portion on the side
of the bypass passage 6. In the hot EGR mode, the four-way selector
valve 14 manipulates the communication among the four exhaust gas
ports to form the bypass passage 6 inside the housing 3.
In the present embodiment, as shown in FIGS. 4 to 6, the four-way
selector valve 14 is capable of continuously rotating in the range
from a bypass full-close position and a bypass full-open position.
Specifically, as shown in FIG. 4, in the cooled EGR mode, the
cooled EGR gas passes at a maximum flow amount in a condition where
the four-way selector valve 14 is in the bypass full-close
position. Alternatively, as shown in FIG. 5 in the hot EGR mode,
the hot EGR gas passes at a maximum flow amount in a condition
where the four-way selector valve 14 is in the bypass full-open
position. FIG. 6 shows an example of a hot-cooled EGR mixing mode
in which the four-way selector valve 14 is in a middle position
between the bypass full-close position and the bypass full-open
position. In this hot-cooled EGR mixing mode, the four-way selector
valve 14 is in a mixing position and the hot EGR gas and the cooled
EGR gas are mixed in the valve chamber 7.
The valve shaft 15 of the EGR selector valve (four-way selector
valve) 14 is formed of a metallic material such as stainless steel
excellent in heat resistance and corrosion resistance. The valve
shaft 15 is in a cylindrical shape and is straightly inserted along
the axial direction of the communication hole from the exterior of
the block 25 of the housing 3 into the valve chamber 7 inside of
the block 25. That is, the valve shaft 15 passes through the
communication hole provided in the block 25 of the housing 3. The
valve shaft 15 has a tip end welded and fixed to the first and
second metal plates 61, 62 of the four-way selector valve 14. The
valve shaft 15 is offset from the center axis of the EGR cooler 1
and the center axis X of the cooler mount face 26 to the center
axis Y of the second EGR port 32 by a predetermined offset amount.
The valve shaft 15 is offset away from the EGR cooler 1 and the
partition 9 of the housing 3 by a predetermined offset amount.
As shown in FIG. 2, the second actuator main body 16 is a
negative-pressure operated actuator which generates driving force
when being applied with negative pressure lower than atmospheric
pressure. The second actuator main body 16 has a rod 63 straightly
extended in the axial direction thereof. The rod 63 is connected
with a link plate (motion converting unit) 64. The link plate 64
converts a linear motion of the rod 63 into a rotary motion of the
valve shaft 15. The link plate 64 has an input end having a fitting
hole. The fitting hole of the link plate 64 is fitted with an axial
tip end of the rod 63 of the second actuator main body 16. The link
plate 64 has an output end having a fitting hole. The fitting hole
of the link plate 64 is fixed with an axial end of the valve shaft
15. The axial end of the valve shaft 15 protrudes outside through
the plug 35.
The second actuator main body 16 has an interior space as a
negative pressure chamber, in which negative pressure is applied,
and an atmospheric pressure chamber opened to the atmosphere. The
second actuator main body 16 accommodates a diaphragm and a spring.
The diaphragm is an elastic component formed of rubber or the like
to be in a film shape. The diaphragm airtightly partitions the
interior space of the second actuator main body 16 into the
negative pressure chamber and the atmospheric pressure chamber. The
spring exerts biasing force to the diaphragm such that the spring
biases the four-way selector valve 14 toward the bypass full-close
position via the diaphragm. The second actuator main body 16 is
connected with a negative pressure pipe 65 through which negative
pressure is applied from an electromotive vacuum pump and a
negative pressure control valve to the negative pressure chamber
The negative pressure control valve has an electromagnetically
controlled structure or an electrically controlled structure.
The negative pressure chamber of the second actuator main body 16
is applied with negative pressure from the electromotive vacuum
pump through a negative-pressure regulator valve. The diaphragm is
displaced in the thickness direction thereof by utilizing pressure
difference between the negative pressure chamber and the
atmospheric pressure chamber. Thereby, the rod 63, which is
interlocked with the diaphragm, is axially moved. The axial
movement of the rod 63 is transmitted to the valve shaft 15 via the
link plate 64, so that the valve shaft 15 rotates by a
predetermined angle. In this operation, the position of the
four-way selector valve 14 is manipulated. The second actuator main
body 16 is fixed to a bracket 66 attached to the housing 3.
The electric motor is a power source for the first actuator main
body 13 of the EGRV. The negative-pressure regulator valve and the
electromotive vacuum pump controls the negative pressure applied to
the negative pressure chamber as a power source of the second
actuator main body 16 of the EGR selector valve. The ECU controls
supplying of electricity to the electric motor, the
negative-pressure regulator valve, and the electromotive vacuum
pump.
The ECU includes a microcomputer including a CPU, a storage unit,
an input circuit, an output circuit, and the like. The CPU executes
control processings and arithmetic processings. The storage unit is
a memory such as a ROM and a RAM that stores programs and data.
When an ignition switch (not shown) is turned ON (IG ON), the ECU
electronically controls the flow control valve 11 and the four-way
selector valve 14 in accordance with the control programs stored in
the storage unit. When the ignition switch is turned OFF (IG OFF),
the control of the ECU is forcedly terminated. The various sensors
output sensor signals, and the sensor signals are A/D converted by
an A/D converter The AND converted signals are input to the
microcomputer of the ECU. The microcomputer is connected with a
crank angle sensor, an accelerator position sensor, a cooling-water
temperature sensor, an intake-air temperature sensor, an EGR flow
sensor, the EGR temperature sensor 49, and the like. The EGR flow
sensor is fixed to a sensor support portion provided in the sensor
cover 55. The EGR temperature sensor 49 is inserted from the
exterior of the block 25 of the housing 3 into the interior of the
block 25.
The ECU compares a detection value of the EGR temperature sensor 49
with normal temperature (reference value), which is estimated from
an engine operating condition such as the cooling-water
temperature, the intake air temperature, the engine rotation speed,
the accelerator position. When the ECU determines that the
detection value of the EGR temperature sensor 49 is equal to or
less than the reference value by a predetermined value, the ECU
determines that the EGR cooler 1 to be deteriorated, and stores the
state in the memory. That is, the EGR temperature sensor 49 also
serves as a temperature sensor for determination of an abnormal
deterioration of the EGR cooler 1. The function of the abnormal
deterioration may be a part of an on board diagnosis (OBD) of an
in-vehicle diagnosis device.
(Operation)
Next, operations of the EGR module incorporated in the EGR system
are described with reference to FIGS. 1 to 6. When the ignition
switch is turned ON (IG ON), and the engine operation is started,
the ECU performs a feedback control of electricity supplied to the
electric motor accommodated in the first actuator main body 13. In
this condition, the ECU controls the electricity supplied to the
electric motor such that the actual position of the EGRV detected
using the EGR flow sensor coincides with a target position, which
is set in accordance with the operating condition of the engine.
The target position corresponds to a target EGR flow amount. When
electricity is supplied to the electric motor, output shaft torque
of the electric motor is transmitted as driving force to the valve
shaft 12. Thus, the flow control valve 11 of the EGRV is
manipulated from the full close position (FIG. 3) in the opening
direction.
The flow control valve 11 of the EGRV is manipulated against
resilience of the spring, and rotated to the valve position
corresponding to the control target. In the present structure,
exhaust gas flows out of the combustion chamber of each engine
cylinder and a part of the exhaust gas is recirculated as hot EGR
from the exhaust passage in an engine exhaust pipe into the intake
passage in the engine intake pipe through an exhaust gas reflux
path. The exhaust gas reflux path includes an EGR passage in the
EGR pipe on the side of the exhaust passage, the first EGR passage
4 inside of the housing 3 of the EGR module, the U-shaped EGR
passage 20 inside of the EGR cooler 1, the second EGR passage 5
inside of the housing 3 of the EGR module, and the EGR passage in
the EGR pipe on the side of the intake passage. The hot EGR gas may
be at temperature higher than 500.degree. C., for example.
When the engine is in a normal operating condition, the ECU
controls the negative-pressure regulator valve and the
electromotive vacuum pump such that the switching position of the
four-way selector valve 14 of the EGR selector valve is in the
bypass full-close position. When electricity supply to the
negative-pressure regulator valve and the electromotive vacuum pump
is turned OFF, for example, the diaphragm is displaced to one side
according to the biasing force of the spring in the second actuator
main body 16; and the rod 63 of the second actuator main body 16 is
positioned in a default position. In this condition, the seal
portion of the four-way selector valve 14 is seated to the first
valve seat portion 51. That is, the position of the four-way
selector valve 14 is switched to the bypass full-close
position.
When the position of the four-way selector valve 14 is switched to
the bypass full-close position to be in the cooled EGR mode, the
inner passage of the housing 3 is set to form a cooled EGR route.
In the cooled EGR mode as shown in FIG. 4, EGR gas returns to the
intake passage through the first EGR passage 4, the EGR cooler 1,
and the second EGR passage 5 in order. Specifically, EGR gas flows
from the EGR introduction port 30 into the housing 3. The EGR gas
passes through the first communication passage 41, the inclined
passage including the valve chamber 7 and the first communication
passage 42, the first EGR port 31, and the U-shaped EGR passage 20
in the EGR cooler 1. The EGR gas further passes through the second
EGR port 32, the bent passage including the second communication
passage 43 and the valve chamber 7, and the second communication
passage 44. Thus, the EGR gas flows out of the housing 3 through
the EGR delivery port 33.
In the present condition, the position of the four-way selector
valve 14 is in the cooled EGR mode in which the flow amount of the
cooled EGR gas is maximum. Therefore, all the EGR gas flowing into
the housing 3 of the EGR module returns to the intake passage after
passing through the EGR cooler 1. Thereby, EGR gas is sufficiently
cooled when passing through the EGR cooler 1, and reduced in
temperature and density to be cooled EGR gas. Thereafter, the
cooled EGR gas is mixed with inlet air in the intake passage.
In the present structure, temperature of combustion in the engine
can be reduced, so that a toxic substance such as nitrogen oxide
(NOx) in exhaust gas can be reduced while maintaining an engine
output. In addition, EGR gas returning to the intake passage is
cooled when passing through the EGR cooler 1, so that charging
efficiency of EGR gas in the combustion chamber of the engine can
be enhanced. Thus, emission of the engine can be further reduced.
When the engine is started in a cold state or regeneration of a
diesel particulate filter (DPF) is performed, the ECU controls the
negative-pressure regulator valve and the electromotive vacuum pump
such that the switching position of the four-way selector valve 14
of the EGR selector valve is in the bypass full-open position. When
electricity supply to the negative-pressure regulator valve and the
electromotive vacuum pump is turned ON, for example, negative
pressure is applied to the negative pressure chamber in the second
actuator main body 16.
A diaphragm 60 moves to the other side corresponding to the
pressure difference between pressure in the negative pressure
chamber and pressure in the atmospheric chamber, so that the rod 63
of the second actuator main body 16 moves to a full-lift position.
The link plate 64 rotates around the axial center of the valve
shaft 15 in conjunction with the linear motion of the rod 63. The
valve shaft 15 fixed to the link plate 64 rotates around the
rotation axis of the valve shaft 15 in conjunction with the
rotation of the link plate 64. Thereby, the four-way selector valve
14 rotates around the rotation axis of the valve shaft 15. The seal
portion of the four-way selector valve 14 is lifted from the first
valve seat portion 51, and is seated to the second valve seat
portion 52. That is, the position of the four-way selector valve 14
is switched to the bypass full-open position.
When the position of the four-way selector valve 14 is switched to
the bypass full-open position to be in the hot EGR mode, the inner
passage of the housing 3 is set to form a hot EGR route. In the hot
EGR mode as shown in FIG. 5, EGR gas returns to the intake passage
by bypassing through the bypass passage 6. Specifically, EGR gas
flows into the housing 3 through the EGR introduction port 30. The
EGR gas further flows through the first communication passage 41,
the bent passage including the valve chamber 7, and the second
communication passage 44. Thus, the EGR gas flows out of the
housing 3 through the EGR delivery port 33.
In the present condition, the position of the four-way selector
valve 14 is in the hot EGR mode in which the flow amount of the hot
EGR gas is maximum. Therefore, all the EGR gas flowing into the
housing 3 of the EGR module returns to the intake passage after
bypassing the EGR cooler 1. In the present operation, intake air
can be sufficiently warmed when the engine is started in a cold
state, so that combustion in the engine can be enhanced. Thus,
exhaust of hydrocarbon (HC) and smoke can be reduced. When
regeneration of the DPF is performed, hot EGR gas can be supplied
to the intake passage. Thereby, intake air drawn into the
combustion chamber can be increased, and exhaust gas flowing
through the DPF can be effectively heated. In the present
operation, hot exhaust gas can be supplied to the DPF, thereby the
DPF can be heated such that temperature of a particulate matter
(PM) can be increased to be combustion temperature in a range
between 500.degree. C. and 650.degree. C., for example. Thus,
regeneration of the DPF can be conducted with low fuel consumption.
In addition, emission can be further reduced by the regeneration of
the DPF.
When temperature of intake air is reduced by cooling EGR gas,
nitrogen oxide (NOx) may be reduced from exhaust gas. However in a
condition where engine speed is low and/or load of the engine is
low, hydrocarbon (HC) in exhaust gas may increase when temperature
of intake air is reduced by cooling EGR gas. Accordingly, the
switching position of the four-way selector valve 14 is set at the
mixing position, in which the rotation angle of the four-way
selector valve 14 is controlled at a proper angle between the
bypass full-close position and the bypass full-open position,
according to the engine operating condition.
When the position of the four-way selector valve 14 is switched to
the mixing position in a hot-cooled EGR mixing mode, the inner
passage of the housing 3 is set to form a hot-cooled EGR gas mixing
route. As shown in FIG. 6, EGR gas flows into the housing 3 through
the EGR introduction port 30. In the present hot-cooled EGR mixing
mode, the EGR gas further flows through both the cooled EGR route,
which includes the first EGR passage 4 and the EGR cooler 1, and
the hot EGR route, which includes the second EGR passage 5 and the
bypass passage 6. Thus, the EGR gas flows out of the housing 3
through the EGR delivery port 33. In the present operation,
temperature of EGR gas returning to the intake passage can be
properly controlled by manipulating a mixing ratio between mixture
of the cooled EGR gas passing through the first EGR passage 4, the
EGR cooler 1, and the second EGR passage 5 and the hot EGR gas
passing through the bypass passage 6. Thus, NOx and HC in exhaust
gas can be simultaneously reduced. The DPF may be regenerated in
the present hot-cooled EGR mixing mode.
(Effects)
In the EGR module incorporated in the EGR system of the present
embodiment, the center of the valve shaft 15 of the four-way
selector valve 14 is offset from the center axis of the EGR cooler
1 and the center axis X of the cooler mount face 26 to the center
axis Y of the second EGR port 32 by a predetermined offset amount.
In addition, the rotation axis of the valve shaft 15 is offset away
from the EGR cooler 1 and the partition 9 of the housing 3 by a
predetermined offset amount.
In the present structure, the rotation axis of the valve shaft 15
of the four-way selector valve 14 and the bypass passage 6 can be
located away from both the cooler mount face 26 of the housing 3
and the partition 9, which extends from the cooler mount face 26 to
the portion in the vicinity of the valve chamber 7. Therefore, the
cooler mount face 26 can be restricted from increasing in
temperature due to transmission of heat from EGR gas passing
through the bypass passage 6 including the first communication
passage 41, the valve chamber 7, and the second communication
passage 44 in the hot EGR mode. In the present structure, the EGR
cooler 1 attached to the cooler mount face 26 can be restricted
from transmitted with heat of hot EGR gas, which flows through the
bypass passage 6 in the hot EGR mode. Therefore, a cooling
performance of the EGR cooler 1 can be maintained in the cooled EGR
mode. Thus, emission can be reduced from exhaust gas in the cooled
EGR mode.
In addition, the rotation axis of the valve shaft 15 of the
four-way selector valve 14 and the bypass passage 6 can be located
away from the cooler mount face 26 and the partition 9 of the
housing 3. Therefore, heat of hot EGR gas, which flows through the
bypass passage 6, can be restricted from exerting influence to
cooled EGR gas, which flows through the second EGR passage 5
including the second communication passage 43 and the valve chamber
7, in the hot-cooled EGR mixing mode. Thus, temperature of cooled
EGR gas, which flows through the second EGR passage 5 can be
maintained. Therefore, temperature control of EGR gas, which
returns to the intake passage, can be facilitated when hot EGR gas
and cooled EGR gas are mixed in the valve chamber 7 of the housing
3. In addition, temperature control of the EGR gas can be
facilitated when hot EGR gas and cooled EGR gas are mixed in the
second communication passage 44 and the exhaust gas reflux path in
the EGR pipe on the side of the intake passage downstream of the
valve chamber 7 with respect to the flow direction of EGR gas.
Thus, emission can be reduced from exhaust gas in the hot-cooled
EGR mixing mode. In the present embodiment, the EGR module includes
the housing 3 joined with the EGR cooler 1 having the U-turn
passage. The housing 3 has the first and second EGR passages 4, 5
defining a shortcut through which EGR gas passes to bypass the EGR
cooler 1, thereby being recirculated to the intake passage.
As referred to FIG. 9 the EGR module disclosed in EP0987427 has the
structure in which the cooler inlet gas passage 121, the cooler
outlet gas passage 122, and the bypass passage 123 are in parallel.
In contrast, in the present embodiment, the housing 3 of the EGR
module can be downsized compared with the housing 102 of the EGR
module in EP0987427. Thus, the EGR module, which includes the EGR
cooler 1 and the valve unit 2, can be downsized. Therefore, a
mounting space needed in an engine room for the EGR module can be
reduced. Thus, the EGR module can be enhanced in mountability to an
engine room of a vehicular such as an automotive. In particular,
the EGR module can be enhanced in mountability to an engine.
In the present structure, the EGR introduction port 30, the EGR
delivery port 33, and the first and second communication passages
41, 44, can be commonly used as the first and second EGR passages
4, 5, which communicate with the EGR cooler 1, and the bypass
passage 6, which bypasses the EGR cooler 1. Therefore, a bypass
passage need not be exclusively provided in the housing 3. Thus,
the number of exhaust ports can be reduced compared with the EGR
module in EP0987427. In addition, the number of switching valves
can be reduced compared with the EGR module in EP0987427.
Therefore, the housing 3 of the EGR module can be downsized. In
addition, the length of the rotation axis of the valve shaft 15 can
be reduced with respect to the axial direction thereof. Thus, the
EGR module can be enhanced in mountability to an engine room of a
vehicular such as an automotive. In particular, the EGR module can
be enhanced in mountability to an engine.
In the present invention, the four-way selector valve 14 of the EGR
selector valve is a butterfly valve constructed of valve plates
each being in a rectangular shape. The valve plates of the four-way
selector valve 14 are extended toward both sides perpendicularly to
the rotation axis of the valve shaft 15. That is, the valve plates
are extended toward both sides along the radial direction of the
rotation axis of the valve shaft 15. The four-way selector valve 14
rotates around the rotation axis of the valve shaft 15 so as to
continuously manipulate the opening area of the two first and
second EGR passages 4, 5 and the opening area of the bypass passage
6. That is, the four-way selector valve 14 continuously manipulates
the flow of cooled EGR gas and the flow of hot EGR gas.
In the present structure, the cooled EGR gas cooled by the EGR
cooler 1 and the hot EGR gas bypassing the EGR cooler 1 can be
efficiently mixed in the vicinity of the valve chamber 7, for
example, inside the second communication passage 44. Therefore, the
temperature control of the EGR gas returning to the intake passage
can be facilitated, so that emission can be effectively
reduced.
In the present embodiment, the EGRV and the EGR selector valve
commonly share the interior of the housing 3 in the EGR module. In
particular, the first EGR passage 4 has the inclined passage
includes the valve chamber 7 and the first communication passage
42. The inclined passage substantially linearly extends from a
portion in the vicinity of the EGR introduction port 30 toward the
first EGR port 31 The inclined passage of the first EGR passage 4
is inclined with respect to the center axis of the first EGR port
31 passing through the center of the first EGR port 31.
In the present structure, exhaust gas flows from the EGR pipe on
the side of an exhaust passage into the first EGR passage 4, and
the exhaust gas further flows substantially straight along the axis
passing through the center of the inclined passage of the first EGR
passage 4. That is, the exhaust gas smoothly passes through the
valve chamber 7 and the first communication passage 42
substantially along the valve face of the four-way selector valve
14, and flows into the inlet of the EGR cooler 1 without bending at
a right angle. In general, the cooled EGR mode is mainly used
compared with the hot EGR mode in an engine operation. That is, in
a normal operation, EGR gas is cooled through the EGR cooler 1 and
recirculated into the intake passage, rather than being bypassed
the EGR cooler 1. In the present structure, pressure loss of ERG
gas can be reduced effectively in the cooled EGR mode, which is
normally set.
Furthermore, the axis of the portion of the partition 9 on the side
of the cooler mount face 26 of the housing 3 is the same as the
center axis of the EGR cooler 1. That is, the portion of the
partition 9 on the side of the cooler mount face 26 extends
continuously from the center axis of the EGR cooler 1. The center
axis of the EGR cooler 1 passes through the center of the EGR
cooler 1. In the present structure, the partition 9 of the housing
3 is capable of equally divide two of the first and second EGR
ports 31, 32 adjacent to the cooler mount face 26 of the housing 3.
In the present structure, pressure loss of EGR gas flow can be
suppressed in the cooled EGR mode in which the EGR gas is cooled by
passing through the EGR cooler 1, and the cooled EGR gas returns to
the intake passage.
In the present embodiment, the center axis of the valve chamber 7
of the housing 3 and the rotation axis of the valve shaft 15 of the
four-way selector valve 14 are offset from both the center axis of
the EGR cooler 1 and the center axis X of the cooler mount face 26
to the center axis Y of the second EGR port 32 by the predetermined
offset amount.
In the present embodiment, as shown in FIG. 1, an imaginary line A
is extended from the lateral side of the housing 3 perpendicularly
to the cooler mount face 26 of the housing 3. That is, the
imaginary line A is extended from the lateral side of the housing 3
in parallel with both the center axis of the EGR cooler 1 and the
center axis X of the cooler mount face 26. An imaginary lines B is
extended from the actuator mount face 36 of the inlet pipe 27 of
the housing 3 in parallel with both the center axis of the EGR
cooler 1 and the center axis X of the cooler mount face 26. The
imaginary lines A, B therebetween define an actuator mount space S
in the housing 3 of the EGR module, and the actuator mount space S
is adapted to accommodating the first actuator main body 13.
In the present structure, the actuator mount space S can be easily
secured around the housing 3. Therefore, the EGR module integrated
with the EGR cooler 1, the EGRV, and the EGR selector valve can be
downsized, compared with EP0987427, in which the EGR module
includes the housing 102 significantly greater than the EGR cooler
101 in width. Furthermore, the size, in particular the width of the
housing 3, which is mounted with the first actuator main body 13,
can be downsized. Thus, the EGR module can be enhanced in
mountability to an engine room of a vehicular such as an
automotive. In particular, the EGR module can be enhanced in
mountability to an engine.
Second Embodiment
As shown in FIGS. 7, 8, in the present embodiment, the block 25 of
the housing 3 has a cooler introduction passage wall (housing wall
section) 71 that partitions the first EGR passage 4 including the
valve chamber 7 and the first communication passage 42 from the
exterior of the block 25. The outer surface of the cooler
introduction passage wall 71 is provided with a radiating portion.
The radiating portion is exposed to the outside of the cooler
introduction passage wall 71. The radiating portion of the cooler
introduction passage wall 71 is provided with multiple radiating
fins (cooling fins) 72. The radiating fins 72 project from the
outer surface of the cooler introduction passage wall 71 to the
opposite side of the first EGR passage 4 including the valve
chamber 7 and the first communication passage 42. The inlet pipe 27
of S the housing 3, the outlet pipe 29, and the Y-shaped partition
wall 45 include bypass passage walls (housing wall portions) 73 to
75 each partitioning the bypass passage 6 from the outside of the
housing 3. The bypass passage 6 includes the EGR introduction port
30, the first communication passage 41, the valve chamber 7, the
second communication passage 44, and the EGR delivery port 33.
In the cooled EGR mode as shown in FIG. 7, temperature of cooled
EGR gas flowing into the EGR cooler 1 is preferably lowered as much
as possible. By contrast, in the hot EGR mode as shown in FIG. 8,
temperature of hot EGR gas is preferably maintained as much as
possible. That is, the preferable conditions in the cooled EGR mode
and the hot EGR mode are opposite from each other. In the present
embodiment, the housing 3 is reduced in thickness, in view of the
foregoing preferable conditions.
Specifically, the thickness of the cooler introduction passage wall
71 of the housing 3 is thinner than the bypass passage walls 73 to
75 by predetermined thickness. In the present structure, heat
resistance relative to hot EGR gas passing through the first EGR
passage 4 including the valve chamber 7 and the first communication
passage 42 is reduced. Furthermore, heat dissipation from the hot
EGR gas to the exterior of the block 25 can be increased. Thus, EGR
gas can be sufficiently cooled, and the sufficiently cooled EGR gas
can be mixed with intake air flowing through the intake passage. In
the present structure, engine combustion temperature can be
reduced, so that a toxic substance such as Nox can be reduced from
exhaust gas, without reducing an engine output. Therefore,
reduction of emission can be further enhanced in the cooled EGR
mode.
Furthermore, the radiating fins 72 are provided to the radiating
portion of the cooler introduction passage wall 71. The radiating
fins 72 project from the outer surface of the cooler introduction
passage wall 71 toward the opposite side of the first exhaust gas
passage. In the present structure, a contact area between the
radiating portion and air flowing over the outer surface of the
cooler introduction passage wall 71 increases That is, the
radiation area of the radiating portion increases. Therefore, hot
EGR gas can be efficiently cooled by using air flowing over the
outer surface of the cooler introduction passage wall 71 when the
hot EGR gas passes through the first EGR passage 4 including the
valve chamber 7 and the first communication passage 42.
Therefore, cooled EGR gas, which returns to the intake passage, can
be air-cooled with not only the EGR cooler 1 but also air flowing
over the outer surface of the cooler introduction passage wall 71.
Thus, the EGR cooler 1 can be downsized. In addition, the EGR
module constructed of the EGR cooler 1 and the valve unit 2 can be
also reduced in size by downsizing the EGR cooler 1. Thus, the EGR
module can be enhanced in mountability to an engine room of a
vehicular such as an automotive. In particular, the EGR module can
be enhanced in mountability to an engine.
The bypass passage walls 73 to 75 of the housing 3 may be thicker
than the cooler introduction passage wall 71 by a predetermined
thickness. In the present structure, thermal capacity of the
housing 3 can be increased relative to hot EGR gas passing through
the bypass passage 6, specifically, the EGR introduction port 30,
the first communication passage 41, the valve chamber 7, the second
communication passage 44, and the EGR delivery port 33. Therefore,
heat dissipation to the exterior of the housing 3 can be reduced.
Thus, temperature of hot EGR gas returning to the intake passage
can be maintained, so that intake air flowing to the engine can be
sufficiently heated when the engine is started in a cold condition.
In the present structure, combustion in the engine can enhanced,
and emission of the engine can be reduced. Thus, a toxic substance
such as hydrocarbon (HC) contained in exhaust gas can be reduced,
so that smoke can be reduced from exhaust gas. An air heat
insulating layer may be provided inside the bypass passage walls 73
to 75 of the housing 3 for heat insulation between hot EGR gas and
ambient air.
(Modification)
In the above embodiments, the EGRV includes the electric actuator
for driving the flow control valve 11 as the valve element of the
EGRV and the electric actuator includes the electric motor and the
transmission device such as reduction gears. Alternatively, the
EGRV may include an electromagnetic actuator or a negative pressure
controlled actuator for driving the flow control valve 11. In this
case, the negative pressure controlled actuator may include a
negative pressure control valve and an electric vacuum pump. The
EGRV may not be mounted to the EGR module. In the above
embodiments, the EGRV is provided upstream of the EGR cooler 1 with
respect to the flow direction of EGR gas. Alternatively, the EGRV
may be provided downstream of the EGR cooler 1 with respect to the
flow direction of EGR gas.
In the above embodiments, the second actuator main body 16 is the
negative pressure controlled actuator provided with the
negative-pressure regulator valve and the electromotive vacuum pump
for driving the four-way selector valve 14 as the valve element of
the EGR selector valve. Alternatively, the second actuator main
body 16 may include an electromagnetic actuator or an electric
actuator for driving the four-way selector valve 14. In this case,
the electric actuator may include an electric motor and a power
transmission device such as reduction gears. The housing 3 of the
valve unit 2 may be provided with a valve biasing device such as a
spring, which biases the four-way selector valve 14 of the EGR
selector valve of the valve unit 2 to the closing direction such
that the four-way selector valve 14 closes the bypass passage 6,
for example.
In the present embodiment, the EGR module is provided with the EGR
cooler 1 of the U-turn flow type, and EGR gas (exhaust gas) flows
through the U-shaped passage inside the EGR cooler 1.
Alternatively, the EGR cooler 1 may have an S-shaped passage or an
I-shaped passage, and EGR gas (exhaust gas) may flow through the
S-shaped passage or the I-shaped passage inside the EGR cooler 1.
In this case, an outlet tank of the exhaust gas cooler connects
with the second EGR port 32 of the housing 3 through a pipe, which
does not conduct heat exchange.
In the above embodiments, the valve chamber 7 communicates with the
EGR introduction port 30 through the first communication passage
41. Alternatively, the first communication passage 41 may be
omitted, and the valve chamber 7 may communicate directly with the
EGR introduction port 30. In the above embodiments, the valve
chamber 7 communicates with the first EGR port 31 through the first
communication passage 42. Alternatively, the first communication
passage 42 may be omitted, and the valve chamber 7 may communicate
directly with the first EGR port 31.
In the above embodiments, the valve chamber 7 communicates with the
second EGR port 32 through the second communication passage 43.
Alternatively, the second communication passage 43 may be omitted,
and the valve chamber 7 may communicate directly with the second
EGR port 32. In the above embodiments, the valve chamber 7
communicates with the EGR delivery port 33 through the second
communication passage 44. Alternatively, the second communication
passage 44 may be omitted, and the valve chamber 7 may communicate
directly with the EGR delivery port 33.
In the above embodiments, the sectional shapes of the EGR
introduction port 30 and the EGR delivery port 33 are circular
shapes. Alternatively, at least one of the sectional shapes of the
EGR introduction port 30 and the EGR delivery port 33 may be a
square shape or a rectangular shape. The sectional shape of the EGR
introduction port 30 may be different from the sectional shape of
the EGR delivery port 33.
In the above embodiments, the sectional shapes of the two first and
second EGR ports 31, 32 are rectangular shapes. Alternatively, at
least one of the sectional shapes of the two first and second EGR
ports 31, 32 may be a square shape or a circular shape. The
sectional shape of the first EGR port 31 may be different from the
sectional shape of the second EGR port 32.
The above structures of the embodiments can be combined as
appropriate.
It should be appreciated that while the processes of the
embodiments of the present invention have been described herein as
including a specific sequence of steps, further alternative
embodiments including various other sequences of these steps and/or
additional steps not disclosed herein are intended to be within the
steps of the present invention.
Various modifications and alternations may be diversely made to the
above embodiments without departing from the spirit of the present
invention.
* * * * *